CN113565837A

CN113565837A - Quick erecting equipment

Info

Publication number: CN113565837A
Application number: CN202010359012.9A
Authority: CN
Inventors: 张春峰; 曾红丰
Original assignee: Beijing Machinery Equipment Research Institute
Current assignee: Beijing Machinery Equipment Research Institute
Priority date: 2020-04-29
Filing date: 2020-04-29
Publication date: 2021-10-29
Anticipated expiration: 2040-04-29
Also published as: CN113565837B

Abstract

The specification provides a quick erecting device, which comprises a base part, an erecting arm, a hydraulic system and a recoil power device; the base part is hinged with the first end of the vertical arm through a first hinge shaft; the hydraulic system comprises a hydraulic control mechanism and a hydraulic cylinder; the recoil power device is arranged on the vertical arm; when the recoil power device works to generate jet flow, the vertical arm rotates around the first hinge shaft in the first direction, and the hydraulic cylinder extends; the hydraulic control mechanism injects oil into the first oil chamber of the hydraulic cylinder in the extension process of the hydraulic cylinder so as to ensure that the first oil chamber is always in a state of completely filling the oil. The power provided by the recoil power device can enable the erecting arm to be matched with the hydraulic system to erect the erecting arm, so that the erecting speed of the erecting arm is ensured; the oil pressure in the hydraulic system can be kept at a relatively small value, and the problem that the oil leakage fault of the hydraulic system is increased due to the fact that the oil pressure is too large in the prior art is solved.

Description

Quick erecting equipment

Technical Field

The invention relates to the technical field of hydraulic pressure, in particular to quick erecting equipment.

Background

To meet the demand for rapid deployment, the hydraulic cylinders in the hydraulic system in erecting (hoisting) equipment such as fire-fighting aerial ladders, missile launch vehicles, etc. should be capable of rapid elongation.

At present, in order to realize the quick extension of a hydraulic cylinder, a hydraulic system of an existing quick erecting system is provided with a high-pressure oil supply branch; a high-pressure energy storage oil tank is arranged in the oil supply branch; when the hydraulic cylinder needs to work quickly to realize the function of erecting quickly, the oil supply branch is communicated with the oil inlet cavity of the hydraulic cylinder, and hydraulic oil flows into the oil inlet cavity from the high-pressure energy storage oil tank in a large flow under the action of high pressure.

Since the high-pressure conventional tank is at a higher pressure than the conventional cylinder, the lines and the various seals of the aforementioned hydraulic system need to withstand a greater pressure, and the likelihood of a leak failure is correspondingly increased.

Disclosure of Invention

The present description provides a quick-raising apparatus that enables a raising arm in a quick-raising apparatus to be raised quickly while hydraulic system pressure remains relatively low.

The specification provides a quick erecting device, which comprises a base part, an erecting arm, a hydraulic system and a recoil power device;

the base part is hinged with the first end of the vertical arm through a first hinge shaft;

the hydraulic system comprises a hydraulic control mechanism and a hydraulic cylinder;

the recoil power device is arranged on the vertical arm;

when the recoil power device works to generate jet flow, the vertical arm rotates around the first hinge shaft in a first direction, and the hydraulic cylinder extends; in the extension process of the hydraulic cylinder, the hydraulic control mechanism injects oil into a first oil cavity of the hydraulic cylinder, so that the first oil cavity is always in a state of being completely filled with the oil.

Optionally, the hydraulic cylinder is hinged to the vertical arm through a second hinge shaft; the recoil power device is arranged on one side, far away from the first hinge shaft, of the second hinge shaft.

Optionally, the direction of the jet ejected by the recoil power device is perpendicular to the extending direction of the rising arm.

Optionally, the recoil power device is a gas power device, a blade propulsion device or a high pressure recoil device.

Optionally, the hydraulic control mechanism comprises a hydraulic pump, an energy storage oil tank, a first two-way valve and a second two-way valve;

one port of the first two-way valve is communicated with an oil outlet of the hydraulic pump, and the other port of the first two-way valve is communicated with the first oil cavity;

one port of the second two-way valve is communicated with the energy storage oil tank, and the other port of the second two-way valve is communicated with the first oil cavity.

Optionally, the first two-way valve is a proportional valve; the hydraulic control mechanism also comprises a proportional overflow valve; and an oil inlet of the proportional overflow valve is communicated with an oil outlet of the hydraulic pump.

Optionally, the hydraulic cylinder is a multi-stage hydraulic cylinder; and a cylinder barrel of the hydraulic cylinder is hinged with the vertical arm through a second hinge shaft.

Optionally, the hydraulic cylinder is a double acting hydraulic cylinder; the hydraulic cylinder further comprises a second oil chamber;

the hydraulic control mechanism further comprises a third two-way valve; the third two-way valve is a proportional valve; and one port of the third two-way valve is communicated with the second oil chamber.

Optionally, the hydraulic control mechanism further comprises a three-position four-way valve; an oil supply port of the three-position four-way valve is communicated with an oil outlet of the hydraulic pump; one oil outlet of the three-position four-way valve is communicated with one port of the first two-way valve, and the other oil outlet of the three-position four-way valve is communicated with one port of the third two-way valve.

Optionally, the hydraulic control mechanism further comprises a fourth two-way valve; the fourth two-way valve is arranged between the hydraulic pump and the energy storage oil tank.

In the rapid erecting equipment provided by the specification, the recoil power device provides power to enable the erecting arm to be matched with the hydraulic system to erect the erecting arm, so that the erecting speed of the erecting arm is ensured; in one case, during operation of the recoil power plant, the hydraulic system is only used to provide sufficient oil to the first oil chamber so that the first oil chamber is in a state of being completely filled with oil; in this case, the oil pressure in the hydraulic system can be kept at a relatively small value, thereby avoiding the problem that the oil pressure in the hydraulic system is large in order to realize the quick lifting of the lifting arm in the prior art, and also avoiding the problem that the oil leakage fault of the hydraulic system is increased in probability due to the excessive oil pressure.

In the invention, the technical schemes can be combined with each other to realize more preferable combination schemes. Additional features and advantages of the invention will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. The objectives and other advantages of the invention will be realized and attained by the structure particularly pointed out in the written description and drawings.

Drawings

The drawings are only for purposes of illustrating particular embodiments and are not to be construed as limiting the invention, wherein like reference numerals are used to designate like parts throughout.

FIG. 1 is a schematic view of a rapid erection device provided by an embodiment;

wherein: 11-base part, 12-vertical arm, 13-hydraulic system, 131-hydraulic cylinder, 131A-first oil chamber, 131B-cylinder barrel, 131C-cylinder sleeve, 131D-second oil chamber, 132-hydraulic pump, 133-energy storage oil tank, 134-first two-way valve, 135-second two-way valve, 136-proportional overflow valve, 137-third two-way valve, 138-three-position four-way valve, 139-fourth two-way valve, 140-conventional oil tank, 141-one-way valve, 14-recoil power device, 15-first articulated shaft, 16-second articulated shaft and 17-third articulated shaft.

Detailed Description

The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate preferred embodiments of the invention and together with the description, serve to explain the principles of the invention and not to limit the scope of the invention.

The embodiment of the specification provides a quick erecting device, so that other power sources are matched with a hydraulic system to realize quick erecting of the device.

FIG. 1 is a schematic diagram of a rapid erection device provided by an embodiment. As shown in fig. 1, the quick-raising apparatus in this embodiment includes a base portion 11, a raising arm 12, a hydraulic system 13, and a recoil power device 14.

As shown in fig. 1, the bed portion 11 is represented by a frame in a general mechanical drawing. The base portion 11 may be a fixed base or a movable base such as a vehicle chassis, and the present embodiment is not particularly limited.

In practical applications, the base portion 11 is mostly a base portion 11 that can be moved, such as a vehicle chassis. Before the quick erecting equipment works, another hydraulic device can be adopted to support the base part 11, so that the stability and the safety of the subsequent operation process are ensured.

The raising arm 12 is a raised arm 12 piece in the quick raising device, and the raising arm 12 is hinged with the base part 11 through a first hinge shaft 15. The actual product form of the raising arm 12 is correspondingly different according to the different fields of use of the quick raising apparatus. In practical application, the erecting arm 12 can be a missile launching canister under the condition that the quick erecting equipment is a missile launching vehicle; in the case of the quick-lift device being a crane or a rescue aerial ladder, the lift arm 12 can be a jib.

The hydraulic system 13 includes a hydraulic cylinder 131 and a hydraulic control mechanism (the hydraulic control mechanism is an integral part of the hydraulic system except the hydraulic cylinder 131). As shown in fig. 1, one end of the hydraulic cylinder 131 is hinged to the raising arm 12 through a second hinge shaft 16, and the other end is hinged to the base portion 11 through a third hinge shaft 17. As known from the prior art and from the application requirements, the second articulation axis 16 and the third articulation axis 17 are parallel to the first articulation axis 15. The hydraulic control mechanism is used for controlling the extension and contraction of the hydraulic cylinder 131, and then controlling the erecting or leveling of the erecting arm 12.

A recoil power device 14 is provided on the rising arm 12. The nozzle of the recoil device is arranged towards the ground. The recoil power device 14 generates a jet when it is operated.

As can be seen from the force correlation, when the jet of the recoil power unit 14 is injected, the jet acts on the recoil power unit 14 with a certain reaction force in the opposite direction. When the velocity of the jet reaches a certain value, the counter-acting force acting on the reflection spray means can overcome the weight of the rising arm 12, so that the rising arm 12 forms a turning moment (or turning momentum) turning around the first hinge axis 15; the raising arm 12 can be raised by being rotated about the first hinge shaft 15 under the action of the rotational moment.

During the operation of the recoil power unit 14 to erect the rising arm 12, the cylinder 131B (or the cylinder rod) of the hydraulic cylinder 131 is extended out of the cylinder 131B by the pulling action of the rising arm 12, so that the first oil chamber 131A of the hydraulic cylinder 131 is increased in volume. When the volume of the first oil chamber 131A is increased, the hydraulic control mechanism injects oil into the first oil chamber 131A, so that the first oil chamber 131A is always in a state of being completely filled with oil, and the phenomenon of empty pulling in the first oil chamber 131A is avoided.

In the present embodiment, at least during the raising of the raising arm 12 to the set state, the recoil power device 14 operates to form a turning moment that turns the raising arm 12 about the first hinge shaft 15.

According to the above description, in the quick erecting device provided in the embodiment of the present disclosure, the power provided by the recoil power device 14 can enable the erecting arm 12 and the hydraulic system 13 to cooperate to erect the erecting arm 12, so as to ensure the erecting speed of the erecting arm 12.

In one operating condition, the rising arm 12 is driven to rotate only by the recoil injection device 14 at the early stage of the rising arm 12. In this initial stage, the hydraulic cylinder is in a passive extension state during the operation of the recoil power unit 14, rather than in an active extension state due to the pressure created by the injection of the oil. At this time, the hydraulic system 13 only needs to supply enough oil to the first oil chamber 131A so that the first oil chamber 131A is in a state of being completely filled with oil, and thus the oil pressure in the entire hydraulic system 13 can be maintained at a relatively small value. Therefore, the problem that the hydraulic pressure of the hydraulic system 13 is large in order to realize the quick lifting of the vertical arm 12 in the prior art can be solved, and the problem that the oil leakage fault occurrence probability of the hydraulic system 13 is increased due to the fact that the hydraulic pressure is too large is solved.

As shown in fig. 1, in the present embodiment, the recoil power device 14 is disposed on a side away from the first hinge shaft 15 with respect to the second hinge shaft 16. Preferably, the recoil power device 14 may be located at the top region of the erector arm 12 to be as far away as possible from the hydraulic cylinder 131 to reduce the effect of the jet stream generated by its operation on the hydraulic system. In other embodiments, the recoil power device 14 may be located elsewhere on the riser arm 12,

in the present embodiment, the injection direction of the recoil power device 14 is preferably set perpendicular to the extending direction of the rising arm 12. It is conceivable that in this case the recoil power device 14 keeps the moment arm at which the erector arm 12 rotates at a stable value; the moment of rotation of the vertical arm 12 is greater for the same amount of recoil.

In other embodiments, the injection direction of the recoil erecting device can be adaptively changed according to the erecting state of the erecting arm 12, so as to realize the excellent erecting control of the erecting arm 12.

For example, in one other embodiment, the injection direction of the recoil raising stem arm 12 may be adaptively changed to urge the raising stem arm 12 to quickly raise in a period when the raising stem arm 12 is just raising, and when the raising stem arm 12 is about to reach the set raising state, the injection direction is changed to decrease the raising speed of the raising stem arm 12, avoiding the raising stem arm 12 from being converted from the resistive load to the overrunning load.

In this embodiment, the backflushing power device 14 is a gas power device, that is, it forms jet flow by gas injection.

In practical application, the gas power device can be a small turbojet engine, a small rocket engine and the like. In other embodiments, the recoil power device 14 may also be a paddle-pusher device, i.e., it may use the rotation of the paddle to drive the jet of air to create the power to rotate the lift arm 12 about the first hinge axis 15. In other embodiments, the recoil power device 14 may also employ a high pressure recoil device formed by high pressure gas.

In the present embodiment, in order to rapidly increase the volume of the first oil chamber 131A in cooperation with the aforementioned operation of the recoil power unit 14, the hydraulic control mechanism should provide an oil supply speed that matches the rate of change in the volume of the first oil chamber 131A.

To match the oil supply speed and the volume change of the first oil chamber 131A, the hydraulic control mechanism is provided with a hydraulic pump 132D, a reservoir tank 133, a first two-way valve 134, and a second two-way valve 135 in the present embodiment.

One port of the first two-way valve 134 is communicated with an oil outlet of the hydraulic pump 132D, and the other port is communicated with a port of the first oil chamber 131A; one port of the second two-way valve 135 communicates with the accumulator tank 133, and the other port also communicates with the port of the first oil chamber 131A.

The accumulator tank 133 stores therein high-pressure oil. In the case where the second two-way valve 135 is opened and the outside pressure is less than the pressure inside the reservoir tank 133, the hydraulic oil of the reservoir tank 133 flows out. In practical applications, the energy storage tank 133 may be provided with a control airbag to achieve the aforementioned functions.

In this embodiment, when the recoil power device 14 works to drive the vertical arm 12 to be vertical, the hydraulic control mechanism can simultaneously supply oil to the first oil chamber 131A in two ways: (1) opening the first two-way valve 134 and pumping oil from the conventional oil tank 140 to the first oil chamber 131A using the hydraulic pump 132D; (2) the second two-way valve 135 is opened, and the oil is caused to flow toward the first oil chamber 131A by the internal pressure of the accumulator tank 133.

It is conceivable that, in cooperation with the foregoing two modes, the hydraulic pump 132D having a smaller maximum unit pumping amount may be employed; the need for a relatively powerful hydraulic pump 132D is eliminated. Of course, in other embodiments, the accumulator tank 133 and the first two-way valve 134 may not be provided if the hydraulic pump 132D can ensure that the amount of pumped oil is sufficient.

In this embodiment, the first two-way valve 134 is a proportional valve to accommodate the rate of change of the volume of the first hydraulic chamber. In practical applications, the oil supply amount of the hydraulic pump 132D to the first oil chamber 131A can be adjusted by adjusting the first two-way valve 134.

Preferably, the first two-way valve 134 may be a proportional directional valve, which has a function of adjusting a flow rate and a function of performing a one-way control by adjustment, so as to prevent hydraulic oil from flowing backward into the hydraulic pump 132D during the injection of hydraulic oil into the first oil chamber 131A.

In the case where the first two-way valve 134 is a proportional valve, the hydraulic control mechanism further includes a proportional relief valve 136. An oil inlet of the proportional relief valve 136 is communicated with an oil outlet of the hydraulic pump 132D. When the hydraulic control mechanism works, the hydraulic pump 132D of the hydraulic control system can maintain a certain working power to ensure constant pumping liquid amount. While first two-way valve 134 reduces the amount of oil passing therethrough, if the outlet port of hydraulic pump 132D is at too high a pressure, proportional spill valve 136 opens to allow excess oil to flow back to conventional oil tank 140.

In the embodiment of the specification, the recoil power device 14 provides large power for erecting the erecting arm 12; in practical application, the final erecting angle of the erecting arm 12 needs to be accurately controlled, and the recoil power device 14 does not adapt to the requirement of accurate erecting angle control, so that the recoil power device 14 is only used in the initial stage of erecting the erecting arm 12; after the erecting arm 12 reaches a certain state, the recoil power device 14 stops working, and the erecting arm 12 is continuously controlled by the hydraulic system until the erecting arm is erected to a set angle. Since the charging oil tank 133 can only provide a small oil pressure and cannot be used for continuously controlling the hydraulic cylinder 131 to push the raising arm 12 to extend after a certain time, it is necessary to disconnect the charging oil tank 133 from the first oil chamber 131A at a proper time point by using the second two-way valve 135 and supply oil to the first oil chamber 131A only by using the hydraulic pump 132D.

As shown in fig. 1, the hydraulic cylinder 131 in this embodiment is a multistage hydraulic cylinder 131. The cylinder 131B of the multistage hydraulic cylinder 131 is hinged to the rising arm 12 via a second hinge shaft 16. According to the operating characteristics of the multi-stage hydraulic cylinder 131, when the first-stage sleeve of the multi-stage hydraulic cylinder 131 extends out of the upper-stage sleeve (or the cylinder 131B), the corresponding hydraulic inference area changes accordingly, and when the hydraulic cylinder 131 extends out of the same length, the volume change amount of the first oil chamber 131A is also different.

In this embodiment, the output power of the recoil power device 14 is large, and after a short period of operation, the raising arm 12 can obtain a large rotation speed. In order to avoid that the recoil power device 14 works such that the hydraulic cylinder 131 produces a large speed change when the cylinder sleeve 131C is fully extended out of the cylinder barrel 131B, which in turn exceeds the vibration impact threshold of the raising arm 12, the recoil power device 14 is used only when the primary sleeve of the hydraulic cylinder 131 is fully extended out of the cylinder barrel 131B.

Specifically, the recoil power device 14 is stopped before the primary sleeve of the hydraulic cylinder 131 is completely extended out of the cylinder 131B. When the primary sleeve of the hydraulic cylinder 131 fully extends out of the cylinder tube 131B, the collision speed of the primary sleeve with the cylinder tube 131B is such that the amount of vibration impact generated by the raising arm 12 is smaller than the vibration impact threshold of the raising arm 12.

In the specific application of the embodiment, the recoil power device 14 can stop the operation of the vertical arm 12 after the vertical arm reaches a certain speed; subsequently, the lift arm 12 continues to rotate about the first hinge axis 15 under its own kinetic energy. During the process that the raising arm 12 continues to rotate by its own kinetic energy, the rate of change in the volume of the first oil chamber 131A gradually decreases to the rated flow rate of the hydraulic pump 132D.

In the present embodiment, a speed sensor that detects the erecting speed of the erecting arm 12 and an angle sensor of the erecting angle may be provided to determine the rate of change in volume of the first oil chamber 131A using the speed sensor and the angle sensor. When the rate of change in the volume of the first oil chamber 131A decreases to the no-load unit pumping amount of the hydraulic pump 132D, the second two-way valve 135 may be closed, and hydraulic oil is pumped to the first oil chamber 131A using only the hydraulic pump 132D by adjusting the first two-way valve 134.

In other embodiments, a pressure sensor that detects the pressure of the oil in the second hydraulic chamber may be provided to determine the opening and closing of the first and second two-

way valves

134 and 135 using the pressure value detected by the pressure sensor, and to control the flow rate of the first two-way valve 134 and the operating state of the hydraulic pump 132D.

In other embodiments, if the output power of the recoil power device 14 can be accurately controlled, the recoil power device 14 can be used when the multi-stage sleeves of the hydraulic cylinders 131 are extended, and the operating states of the first two-way valve 134, the second two-way valve 135 and the hydraulic pump 132D can be adaptively controlled.

In this embodiment, the hydraulic cylinder 131 is a multi-stage hydraulic cylinder 131. In other embodiments, the hydraulic cylinder 131 may be a single-stage hydraulic cylinder 131.

As described above, in the present embodiment, the cylinder 131B of the multistage hydraulic cylinder 131 is hinged to the raising arm 12 via the second hinge shaft 16. This arrangement ensures that the first-stage cylinder 131B (i.e., the cylinder 131B having the largest diameter) of the multi-stage hydraulic cylinder 131 is first extended. Of course, in other embodiments, if the thinnest cylinder sleeve 131C (or cylinder rod) of the multi-stage hydraulic cylinder 131 has sufficient supporting strength, it is also possible to make the thinnest cylinder sleeve 131C (or cylinder rod) of the multi-stage hydraulic cylinder 131 hinge with the rising arm 12 through the second hinge shaft 16.

As shown in fig. 1, the hydraulic cylinder 131 in this embodiment is a double-acting cylinder. The hydraulic control mechanism further includes a third two-way valve 137. The third two-way valve 137 is also a proportional valve, and one port of the third two-way valve 137 is communicated with the second oil chamber 131D; during erection of the erecting arm 12, the third two-way valve 137 is opened, and the hydraulic oil in the second oil chamber 131D in the double-acting cylinder flows back to the conventional oil tank 140 through the third two-way valve 137.

In practical application, in order to avoid the change from the resistance load to the overrunning load of the raising arm 12, before the raising arm 12 reaches the eversion point, the third two-way valve 137 is controlled to change the oil outflow rate of the second oil chamber 131D, so that the second oil chamber 131D forms a certain back pressure to slow down the moving speed of the raising arm 12, and then the precise control of the raising angle of the raising arm 12 is realized by precisely controlling the oil backflow amount.

In this embodiment, the hydraulic control mechanism further includes a three-position, four-way valve 138. An oil supply port of the three-position four-way valve 138 is communicated with an oil outlet of the hydraulic pump 132D, one oil outlet of the three-position four-way valve 138 is communicated with one port of the first two-way valve 134, and the other oil outlet is communicated with one port of the third two-way valve 137; the return of three-position, four-way valve 138 is in communication with a conventional sump 140.

In this embodiment, the three-position four-way valve 138 is an O-type valve. During raising of the raising arm 12, the three-position four-way valve 138 is in a state such that the oil outlet of the hydraulic pump 132D is communicated with one port of the first two-way valve 134, and such that one port of the third two-way valve 137 is communicated with the normal oil tank 140; while during the leveling back of the raising arm 12, the three-position four-way valve 138 is in the other state, so that the outlet port of the hydraulic pump 132D communicates with one port of the third two-way valve 137, so that one port of the second two-way valve 135 communicates with the conventional oil tank 140.

Of course, according to the practical application, the three-position four-way valve 138 in this embodiment may also be another type of three-position four-way valve 138, and this embodiment is not limited.

With continued reference to fig. 1, in the present embodiment, the hydraulic control mechanism further includes a fourth two-way valve 139. The fourth two-way valve 139 is provided between the hydraulic pump 132D and the charge oil tank 133. Before the raising operation of the raising arm 12 is performed, the fourth two-way valve 139 is opened, and the hydraulic pump 132D operates to pump oil into the energy storage oil tank 133, thereby storing energy in the oil.

In addition to having the foregoing structure, the hydraulic control mechanism of the present embodiment further includes a check valve 141141, the position of which is shown in fig. 1.

The above description is only for the preferred embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention are included in the scope of the present invention.

Claims

1. The quick erecting equipment is characterized by comprising a base part, an erecting arm, a hydraulic system and a recoil power device;

the recoil power device is arranged on the vertical arm;

2. The rapid erecting apparatus as recited in claim 1, wherein:

the hydraulic cylinder is hinged with the vertical arm through a second hinge shaft; the recoil power device is arranged on one side, far away from the first hinge shaft, of the second hinge shaft.

3. The rapid erecting device as recited in claim 2, wherein:

the direction of jet flow sprayed by the recoil power device is perpendicular to the extending direction of the vertical arm.

4. The rapid erecting device according to any one of claims 1 to 3, wherein:

the recoil power device is a gas power device, a blade pushing device or a high-pressure recoil device.

5. The rapid erecting device according to any one of claims 1 to 3, wherein:

the hydraulic control mechanism comprises a hydraulic pump, an energy storage oil tank, a first two-way valve and a second two-way valve;

6. The rapid erecting apparatus as recited in claim 5, wherein:

the first two-way valve is a proportional valve; the hydraulic control mechanism also comprises a proportional overflow valve; and an oil inlet of the proportional overflow valve is communicated with an oil outlet of the hydraulic pump.

7. The rapid erecting apparatus as recited in claim 5, wherein:

the hydraulic cylinder is a multi-stage hydraulic cylinder; and a cylinder barrel of the hydraulic cylinder is hinged with the vertical arm through a second hinge shaft.

8. The rapid erecting apparatus as recited in claim 5, wherein:

the hydraulic cylinder is a double-acting hydraulic cylinder; the hydraulic cylinder further comprises a second oil chamber;

9. The rapid erecting apparatus as recited in claim 8, wherein:

the hydraulic control mechanism also comprises a three-position four-way valve; an oil supply port of the three-position four-way valve is communicated with an oil outlet of the hydraulic pump; one oil outlet of the three-position four-way valve is communicated with one port of the first two-way valve, and the other oil outlet of the three-position four-way valve is communicated with one port of the third two-way valve.

10. The rapid erecting apparatus as recited in claim 5, wherein:

the hydraulic control mechanism further comprises a fourth two-way valve; the fourth two-way valve is arranged between the hydraulic pump and the energy storage oil tank.